JP2004205057A - Plate type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase the overall heat radiating performance by uniformly flowing internal fluid in the parts of inner fins in a plate type heat exchanger having the inner fins. <P>SOLUTION: Corrugated surfaces 5 and 6 formed with corrugation tilted relative to a lateral direction and crossed each other are disposed near the access ports of a first plate 3 and a second plate 4 having access ports 1 and 2 disposed both ends parts thereof in the longitudinal direction. Flat surfaces 7 are formed in an intermediate part between the first plate 3 and the second plate 4, and inner fins 9 are disposed between the flat surfaces 7. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention provides a flat channel inside by joining the edges of a pair of plates formed in a dish shape with their edges raised to form a flat channel inside, and providing a fluid inlet / outlet at both ends thereof, The present invention relates to a so-called Dron cup type heat exchanger in which an inner fin is interposed in a portion, and particularly to a device in which a fluid is uniformly circulated in each portion of the inner fin.
[0002]
[Prior art]
The Dron cup type heat exchanger has a pair of plates at least one of which is formed in a dish shape, has inner fins interposed therein, and has a fluid inlet / outlet at both ends. Then, a liquid such as oil flows through one of the inlets and outlets, passes through the flat inside, and is guided to the other inlet and outlet, during which heat exchange is performed between the internal fluid and the fluid outside the plate. Such a plate-type heat exchanger has a drawback in that the fluid flows most easily in the vicinity immediately above the pair of entrances and exits, and the fluid hardly flows as the distance from the straight line increases in the width direction.
[0003]
Therefore, a proposal has been made in which a fin for fluid diffusion is arranged at an end where an entrance and an exit are present, and a fluid is uniformly circulated through each part (for example, see Patent Document 1).
In this arrangement, diffusion fins are arranged near the entrance and exit of the plate to allow the internal fluid to flow in the width direction of the plate, and fin rows are arranged in the middle of the plate in a direction perpendicular to the plate.
Further, as another prior art, there has been proposed an arrangement in which a pair of upper and lower plates are provided with punches extending in the radial direction around the entrance of the plate in the same direction, and the punches come into contact with each other to form a partition shape ( For example, see Patent Document 2.)
[0004]
[Patent Document 1]
JP-A-59-37985 [Patent Document 2]
Published Japanese Utility Model Application No. 59-37986
[Problems to be solved by the invention]
The plate-type heat exchanger according to Patent Document 1 needs to separately manufacture a diffusion fin at a fluid inlet / outlet portion and a fin at an intermediate portion, and separately install the fins in a plate. There was a drawback that assembly was troublesome.
Next, the plate-type heat exchanger according to Patent Literature 2 has a feature that the number of parts is smaller than that of the former one and is easy to assemble since the punching grooves are formed radially in the plate itself to partition the plate. is there. However, even if such a radiation groove is provided, a large amount of fluid eventually circulates along a line that linearly connects the pair of entrances and exits, and the point of difficulty in circulating along the periphery cannot be improved much.
Accordingly, it is an object of the present invention to provide a plate fin type heat exchanger capable of reliably diffusing a fluid in the width direction at the entrance and exit and further promoting heat exchange at the entrance and exit.
[0006]
[Means for Solving the Problems]
According to the present invention, a pair of a first plate (3) and a second plate (4), at least one of which is formed in a dish shape and has entrances (1) and (2) formed at both ends in the longitudinal direction, is provided. A plate-type heat exchanger in which the edges of both plates (3) and (4) are liquid-tightly joined to each other to form a flat flow path inside,
In both plates (3) and (4), corrugated surfaces (5) and (6) are formed at both ends in the longitudinal direction, and a flat surface (7) is formed at an intermediate portion.
The corrugated surfaces (5) and (6) of both plates (3) and (4) have a large number of inclined wave ridges (8) and (8a) arranged in parallel to the width direction of the plates,
The corrugated surfaces (5) and (6) of the opposing plates (3) and (4) are arranged such that their ridge lines (8) and (8a) intersect with each other,
An inner fin (9) is interposed between the flat surfaces (7) of the opposed plates (3) and (4) to provide a plate-type heat exchanger.
[0007]
The present invention described in claim 2 is based on claim 1,
The corrugated surfaces (5) and (6) of both plates (3) and (4) have a flat C-shape around the entrances (1) and (2) with respect to a center line parallel to the longitudinal direction of the plates. Or a number of inverted U-shaped wave ridges (8) (8a) are juxtaposed,
The corrugated surfaces (5) and (6) of the opposing plates (3) and (4) are plate-type heat exchangers arranged such that their ridges (8) and (8a) cross each other.
[0008]
According to a third aspect of the present invention, in the first or second aspect,
The ridgelines (8) and (8a) of the waves on the wavy curved surfaces (5) and (6) of both plates (3) and (4) are at 60 to 80 degrees with respect to a center line parallel to the longitudinal direction of the plates. It is a plate type heat exchanger formed at an angle.
The present invention described in claim 4 is the invention according to any one of claims 1 to 3,
The corrugated surfaces (5) and (6) of both plates (3) and (4) are plate-type heat exchangers brazed to each other at their intersections.
[0009]
BEST MODE FOR CARRYING OUT THE INVENTION
Next, an embodiment of the present invention will be described with reference to the drawings.
1 is a partially cutaway front view of the plate heat exchanger of the present invention, FIG. 2 is a schematic cross-sectional view taken along the line II-II of FIG. 1, and FIG. 3 is an example of an inner fin 9 used in the heat exchanger. FIG. 4 is a schematic sectional view taken along line IV-IV of FIG.
[0010]
This example includes a pair of upper and lower dish-shaped first and third plates 3 and 4 whose outer circumferences are substantially square (or may be oval) and are aligned with each other, and an inner fin 9 interposed therebetween. The outer periphery of each of the first plate 3 and the second plate 4 is raised and formed in a shallow dish shape. In this example, the first plate 3 is fitted to the outer periphery of the opening end of the second plate 4. In addition, both may be provided with a small flange (not shown) at the opening edge, and the small flanges (including the outer flange and the inner flange) may be configured to contact each other. In this example, a pair of entrances and exits 1 and 2 are formed at the center in the width direction of both ends in the longitudinal direction of the first plate 3.
[0011]
Next, at both end portions of the first plate 3 and the second plate 4, except for the entrance 1, there are arranged wavy curved surfaces 5, 6 in a U-shape or an inverted C shape. That is, the first plate 3 is formed with an inverted C-shaped wavy curved surface 5, and the second plate 4 is formed with a U-shaped wavy bent surface 6. Therefore, the wavy curved surface 5 of the first plate 3 and the wavy curved surface 6 of the second plate 4 are opposite to each other. Each angle is formed at 60 ° to 80 ° with respect to a center line parallel to the longitudinal direction. That is, in FIG. 4, the ridge line 8 a of each wave of the wave-shaped curved surface 6 and each θ that forms the center line are 60 ° to 80 °.
[0012]
Next, an intermediate portion between the first plate 3 and the second plate 4 is formed with a flat surface 7. Then, as shown in FIG. 2, an inner fin 9 shown in FIG. 3 is interposed between the flat surfaces 7 in the pair of upper and lower first plates 3 and second plate 4, for example. At this time, the ridge lines of the corrugated curved surfaces 5 and 6 of the opposing plates 3 and 4 intersect with each other, and the intersections contact each other.
At least one surface of each of the first plate 3 and the second plate 4 is assembled with a brazing material covered or interposed. Then, the whole is inserted into a high-temperature furnace, and the contact portions are brazed and fixed to each other.
[0013]
In this heat exchanger core, as an example, a high-temperature fluid such as oil flows between the two plates 3 and 4 from one of the ports 1, and a low-temperature fluid such as cooling water flows into the outer surfaces of the first plate 3 and the second plate 4. Distribute. The liquid that has flowed in from the inlet / outlet 1 moves to the right while diffusing in the width direction in a zigzag manner along grooves that intersect each other at the corrugated curved surfaces 5 and 6. Then, it flows through the inner fins 9 to reach the wavy curved surfaces 5 and 6 at the right end, and flows in a zigzag shape in both grooves to flow out of the other entrance 2. And it is cooled by cooling water etc. between them. This cooling is effectively performed not only during the flat surface 7, but also during the flow through the corrugated surfaces 5 and 6.
[0014]
In this example, the relationship between the wave angles θ of the curved surfaces 5 and 6 and the heat radiation performance is as shown in FIG. That is, the angle (wave angle θ) between the center line of each plate and the ridge line of the wave rapidly increases from 0 to 60 ° when the angle gradually increases, and gradually increases above 60 °. I do. In addition, the heat radiation performance rapidly decreases at a position slightly exceeding 80 °. This means that the heat radiation performance tends to increase as θ increases, but at the same time, the pressure loss also increases, and when the angle becomes approximately 90 °, the flow is interrupted and the heat radiation performance rapidly decreases.
Next, when looking at the increase rate of the heat radiation performance with respect to the increase rate of the pressure loss, as shown in FIG. 7 and 8 that the wave angle θ is most effective in the range of 60 ° to 80 °. Therefore, according to one aspect of the present invention, the wave angle falls within this range.
[0015]
Next, FIG. 5 is a front view of a plate-type heat exchanger showing a second embodiment of the present invention, and FIG. 6 is a sectional view taken along the line VI-VI of FIG.
This example is different from those of FIGS. 1 and 2 in that a pair of entrances 1 and 2a and entrances 2 and 1a are formed at both ends of the first plate 3 and the second plate 4, respectively. Then, a large number of first plates 3 and second plates 4 are stacked, and the first fluid 10 and the second fluid 11 alternately flow in every other plate. That is, in FIGS. 5 and 6, the first fluid 10 flows between the ports 1 and 2, and the second fluid 11 flows between the ports 1a and 2a.
[0016]
Therefore, in FIG. 5, the entrances and exits 1 a and 2 a of the second plate 4 are recessed at the edge of the hole and come into contact with the edge of the hole of the first plate 3. Then, the second fluid 11 flows on the lower surface side of the first plate 3. The entrances 1 and 2 of the second plate 4 are located at the same position as the flat surface 7, and the first fluid 10 flows in from the entrance 1, and in this example, the second plate 4 on the top surface and the first plate 3 opposed thereto During this time, the first fluid 10 flows. Then, the second fluid 11 flows between the entrance 2 a and the entrance 1 a on the lower surface side of the first plate 3. Then, heat exchange is performed between the first fluid 10 and the second fluid 11.
[0017]
Although FIGS. 5 and 6 show a so-called stack type heat exchanger, the present invention is not limited to this. Also in this example, the second fluid 11 and the first fluid 10 are diffused and flow in the width direction at both ends of the first plate 3 and the second plate 4, respectively, and the fluid flows uniformly in each part of the inner fin 9. At the same time, stirring is performed at the corrugated surfaces 5, 6 of the first plate 3 and the second plate 4, and heat exchange is promoted at both ends.
[0018]
Next, FIG. 9 shows still another embodiment of the present invention. This embodiment is different from that of FIG. 1 in that the directions of the wave-shaped bent surfaces 5, 6 are all formed in the same direction with respect to the width direction. That is.
In addition, the wavy curved surface 5 of the first plate 3 and the wavy curved surface 6 of the second plate 4 are opposite to each other, and their ridge lines cross each other.
[0019]
[Action and Effect of the Invention]
In the plate heat exchanger of the present invention, corrugated surfaces 5 and 6 are formed at both longitudinal ends of the first plate 3 and the second plate 4, and a flat surface 7 is formed at an intermediate portion. Each of the wave-shaped curved surfaces 5 and 6 has a large number of wave ridges 8 and 8a that are inclined with respect to the width direction of the plate arranged in parallel. Since the fluids are formed so as to intersect with each other, the fluid flowing in and out of the entrances 1 and 2 located at both ends moves along the wave ridge direction of the first plate 3 and the second plate 4 and faces each other. Diffusion in the width direction due to ridges.
[0020]
That is, the fluid flowing between the two by the pair of upper and lower waves crossing each other circulates in a zigzag manner, and spreads uniformly at both ends of each plate. Thereby, the fluid can uniformly flow in from both end edges of the inner fin 9 existing between the flat surfaces 7, and the heat exchange performance can be improved.
In addition, the first plate 3 and the second plate 4 have the effect of promoting heat exchange by stirring the fluid due to the presence of the corrugated curved surfaces 5 and 6 intersecting each other.
[Brief description of the drawings]
FIG. 1 is a partially cutaway front view showing a first embodiment of a plate heat exchanger of the present invention.
FIG. 2 is a sectional view taken along the line II-II of FIG.
FIG. 3 is an essential part perspective view showing an example of an inner fin 9 used in the heat exchanger.
FIG. 4 is a sectional view taken along the line IV-IV in FIG. 2;
FIG. 5 is a front view showing a second embodiment of the plate heat exchanger of the present invention.
6 is a sectional view taken along the line VI-VI in FIG. 5;
FIG. 7 is an explanatory diagram showing the relationship between the wave angle θ and the heat radiation performance on the curved wave surfaces 5 and 6 of the present invention.
FIG. 8 is an explanatory diagram showing the wave angle θ as a horizontal axis, and a vertical axis showing a heat radiation performance increase ratio with respect to a pressure loss increase ratio.
FIG. 9 is a front view showing a plate-type heat exchanger according to a third embodiment of the present invention.
[Explanation of symbols]
1, 1a, 2, 2a Doorway 3 First plate 4 Second plate 5, 6 Wavy curved surface 7 Flat surface 8 Ridge 8a Ridge 9 Inner fin
10 First fluid
11 Second fluid

Claims (4)

At least one has a pair of first plate (3) and a second plate (4) formed in a dish shape and formed with entrances (1) and (2) at both ends in the longitudinal direction,
In a plate heat exchanger in which the edges of both plates (3) and (4) are liquid-tightly joined to each other and a flat flow path is formed inside,
In both plates (3) and (4), corrugated surfaces (5) and (6) are formed at both ends in the longitudinal direction, and a flat surface (7) is formed at an intermediate portion.
The corrugated surfaces (5) and (6) of both plates (3) and (4) have a large number of inclined wave ridges (8) and (8a) arranged in parallel to the width direction of the plates,
The corrugated surfaces (5) and (6) of the opposing plates (3) and (4) are arranged such that their ridge lines (8) and (8a) intersect with each other,
An inner fin (9) is interposed between the flat surfaces (7) of the opposed plates (3) and (4). In claim 1,
The corrugated surfaces (5) and (6) of both plates (3) and (4) have a flat C-shape around the entrances (1) and (2) with respect to a center line parallel to the longitudinal direction of the plates. Or a number of inverted U-shaped wave ridges (8) (8a) are juxtaposed,
A plate-type heat exchanger wherein the corrugated surfaces (5) and (6) of the opposing plates (3) and (4) are arranged such that their ridges (8) and (8a) cross each other. In claim 1 or claim 2,
The ridgelines (8) and (8a) of the waves on the wavy curved surfaces (5) and (6) of both plates (3) and (4) are at 60 to 80 degrees with respect to a center line parallel to the longitudinal direction of the plates. Plate heat exchanger formed at an angle. In any one of claims 1 to 3,
A plate heat exchanger in which the corrugated surfaces (5) and (6) of both plates (3) and (4) are brazed to each other at their intersections.

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